JP2006002585A - Centrifugal fan and air conditioner using the same - Google Patents

Centrifugal fan and air conditioner using the same Download PDF

Info

Publication number
JP2006002585A
JP2006002585A JP2004176867A JP2004176867A JP2006002585A JP 2006002585 A JP2006002585 A JP 2006002585A JP 2004176867 A JP2004176867 A JP 2004176867A JP 2004176867 A JP2004176867 A JP 2004176867A JP 2006002585 A JP2006002585 A JP 2006002585A
Authority
JP
Japan
Prior art keywords
blade
main plate
centrifugal fan
curved
fan
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2004176867A
Other languages
Japanese (ja)
Other versions
JP4308718B2 (en
Inventor
Akira Takushima
多久島　朗
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Samsung Electronics Co Ltd
Original Assignee
Samsung Electronics Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Samsung Electronics Co Ltd filed Critical Samsung Electronics Co Ltd
Priority to JP2004176867A priority Critical patent/JP4308718B2/en
Priority to KR1020040085044A priority patent/KR100635851B1/en
Priority to CNB2005100052543A priority patent/CN100504073C/en
Publication of JP2006002585A publication Critical patent/JP2006002585A/en
Application granted granted Critical
Publication of JP4308718B2 publication Critical patent/JP4308718B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/02—Selection of particular materials
    • F04D29/026—Selection of particular materials especially adapted for liquid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S416/00—Fluid reaction surfaces, i.e. impellers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a centrifugal fan capable of increasing marketability by suppressing noise while reducing cost, and an air conditioner using the centrifugal fan. <P>SOLUTION: This centrifugal fan comprises a main plate 11 rotatable in a prescribed direction P around a rotating axis O and vanes 4 disposed on the main plate 11. The cross sections of the vanes 4 at the same radial position of the main plate 11 including at least the trailing edge 7 positioned on the outer peripheral side of the main plate 11 are curved to be projected in the anti-rotating direction (-P direction) of the main plate 11. The curve is gradually increased from the leading edge 6 to the trailing edge 7 of the vanes 4. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、回転軸線周りに所定方向に回転可能な主板と、該主板に配設される翼とを備える遠心ファンおよびこれを用いた空気調和機に関するものである。   The present invention relates to a centrifugal fan including a main plate that can rotate in a predetermined direction around a rotation axis, and a blade disposed on the main plate, and an air conditioner using the centrifugal fan.

従来におけるベーシックな遠心ファンとしては、例えば図６に示すものが知られている。同図に示す遠心ファン１０１は、ボス１０３と、該ボス１０３の一端側に回転軸線を一致させて配設される主板１１１と、この主板１１１に配設されるファンブレード（翼）１０４とを備えている。ファンブレード１０４の上方には、ベルマウス１０８とその上端側で配置されるケーシング１０９とが設けられている。   As a conventional basic centrifugal fan, for example, the one shown in FIG. 6 is known. The centrifugal fan 101 shown in FIG. 1 includes a boss 103, a main plate 111 disposed on one end side of the boss 103 with the rotation axis aligned, and a fan blade (blade) 104 disposed on the main plate 111. I have. Above the fan blade 104, a bell mouth 108 and a casing 109 disposed on the upper end side thereof are provided.

このような遠心ファン１０１のボス１０３を所定方向Ｐ（この場合は反時計回り）に回転させてファンブレード１０４を旋回させることで、流体（例えば空気）を矢印Ｍのようにベルマウス１０８の開口部を介して遠心ファン１０１内に流入させて、ファンブレード１０４の外周側に矢印Ｎのように送り出している。   By rotating the boss 103 of the centrifugal fan 101 in a predetermined direction P (in this case, counterclockwise) and turning the fan blade 104, fluid (for example, air) is opened in the bell mouth 108 as indicated by an arrow M. The air flows into the centrifugal fan 101 through the section and is sent out to the outer peripheral side of the fan blade 104 as indicated by an arrow N.

しかしながら、遠心ファン１０１のファンブレード１０４を旋回させたときに、図７に示すように、ファンブレード１０４で翼端渦Ｓが発生する。この翼端渦Ｓが自翼または他翼の面、ベルマウス１０８などの構造物に衝突して干渉すると、騒音が発生して空力損失が増大してしまう。また、遠心ファン１０１は吸い込み流れに対し吹き出し流れがほぼ直角に曲げられるため、流れは主板１１１側に偏りがちとなる。すなわち、ファンブレード１０４の翼面のうち、主板１１１と反対の外周近傍での送風が行われにくく（図８のＷＨ、ＷＬ）、その結果、ファン効率の低下、必要回転数の上昇による送風音の増大、吹き出し流れの偏流による下流側通路の送風抵抗の増大などの問題が生じてしまう。このような事態の防止を図るために、以下に示すような技術が提案されている。   However, when the fan blade 104 of the centrifugal fan 101 is swung, a blade tip vortex S is generated in the fan blade 104 as shown in FIG. When the tip vortex S collides with and interferes with the structure of the own wing or the other wing, the bell mouth 108 or the like, noise is generated and aerodynamic loss increases. Further, since the blowout flow is bent at a substantially right angle with respect to the suction flow, the flow tends to be biased toward the main plate 111 side. In other words, it is difficult to blow air near the outer periphery of the blade surface of the fan blade 104 opposite to the main plate 111 (WH, WL in FIG. 8), and as a result, the fan noise decreases and the blowing noise due to an increase in the required rotational speed. And an increase in the blowing resistance of the downstream passage due to the drift of the blowout flow will occur. In order to prevent such a situation, the following techniques have been proposed.

例えば、図９に示すように、ファンブレード１０４の上側に、主板１１１と対向するようにシュラウド１２１を装着してなる遠心ファン１２０が提案されている。このようにすることで、ファンブレード１０４の上流側から翼端渦Ｓが漏れ出ることを防止できるとともに、翼面の傾斜による流れの均一化を図っている。この種の技術として、シュラウドとの角部を埋めて滑らかな形状としたもの（特許文献１参照）や、ファンブレードの主板側端部に対し、その反対側の翼端部を反回転方向にオフセットしてファンブレードを傾斜させるもの（特許文献２参照）が提案されている。   For example, as shown in FIG. 9, a centrifugal fan 120 in which a shroud 121 is mounted on the upper side of the fan blade 104 so as to face the main plate 111 has been proposed. By doing so, the blade tip vortex S can be prevented from leaking from the upstream side of the fan blade 104, and the flow can be made uniform by the inclination of the blade surface. As this kind of technology, the corner with the shroud is filled to make it a smooth shape (see Patent Document 1), or the blade end on the opposite side of the fan blade on the main plate side is in the counter-rotating direction. There has been proposed one that tilts a fan blade by offsetting (see Patent Document 2).

また、図１０、図１１に示すように、ファンブレード１０４の上側に設けられるケーシング１３１を、ファンブレード１０４に近接させて取り付けることで、ファンブレード１０４の上流側から翼端渦Ｓが漏れ出ることを防止する遠心ファン１３０が提案されている。
特開２００１−１４０７８９号公報 特開平５−３９９３０号公報 Also, as shown in FIGS. 10 and 11, the tip 131 is leaked from the upstream side of the fan blade 104 by attaching the casing 131 provided on the upper side of the fan blade 104 in the vicinity of the fan blade 104. A centrifugal fan 130 for preventing the above has been proposed.
JP 2001-140789 A JP-A-5-39930

しかしながら、従来の技術においては、以下のような問題がある。すなわち、シュラウドを付設する構成とすると、部品点数が増大するとともに、シュラウドは主板やファンブレードとは別に成形する必要があり、シュラウドの接合加工作業が必要となるため、コストや作業負担が大幅に上昇してしまうという問題がある。
一方、ケーシングをファンブレードに近接させる構成としたものについては、図１２に示すように、ファンブレード１０４の上流側から漏れる流れＴとケーシング１３１との干渉（同図の衝突箇所Ｕ）により送風音が増大してしまい、商品性が低下する、という問題ある。 However, the conventional techniques have the following problems. In other words, the configuration with the shroud increases the number of parts, and the shroud needs to be molded separately from the main plate and fan blade, and the shroud joining work is required, which greatly increases the cost and work load. There is a problem of rising.
On the other hand, in the case where the casing is configured to be close to the fan blade, as shown in FIG. 12, the blowing sound is caused by the interference between the flow T leaking from the upstream side of the fan blade 104 and the casing 131 (collision point U in the figure). Increases, resulting in a problem that the merchantability is reduced.

従って、本発明は、コストを低減しつつ騒音を抑えて商品性を高めることができる遠心ファンおよびこれを用いた空気調和機を提供することを目的とする。   Therefore, an object of this invention is to provide the centrifugal fan which can suppress a noise, and can improve commercial property, reducing cost, and an air conditioner using the same.

請求項１に係る発明は、回転軸線周りに所定方向に回転可能な主板と、該主板から立ち上がり、かつ該主板の径方向内方から外方へ延在するように設けられ、該主板に前記回転軸線周りに配置された複数の翼とを備え、前記翼の少なくとも前記主板の外周側に位置する後縁を含む前記主板の同一半径位置における翼断面が前記主板の反回転方向に突出するように湾曲されてなり、かつ、その湾曲は前記翼の前縁側から後縁にかけて次第に大きくなっていることを特徴とする。   The invention according to claim 1 is provided so as to be able to rotate in a predetermined direction around a rotation axis, and to stand up from the main plate and extend from the inside in the radial direction of the main plate to the outside. A plurality of blades arranged around the rotation axis, and a blade section at the same radial position of the main plate including a trailing edge located at least on the outer peripheral side of the main plate protrudes in the counter-rotating direction of the main plate. And the curve gradually increases from the leading edge side to the trailing edge of the blade.

この発明によれば、前記翼断面を前記主板の反回転方向に突出するように湾曲したことにより、前記主板を所定方向に回転させた際に、前記翼の前縁から後縁にかけて発生する流体の流れを、前記翼の湾曲した部位に向けることができる。よって、前記湾曲した部位を前記翼の回転軸線方向中央付近に形成することで、流体の流れを前記翼の回転軸線方向中央付近に向けることができ、前記翼からの流体の吹き出し速度を前記翼の回転軸線方向中央付近で速めることができるため、前記翼に対する流体の相対速度を前記翼の回転軸線方向に渡って均一化することができる。また、流体の流れを前記翼の回転軸線方向中央付近に向けることで、前記羽根における前記主板と反対側の翼端部への漏れ流れを抑制することができ、翼端渦の増大を抑制することができる。従って、シュラウドを用いることなく、前記翼の翼端渦を低減することができ、コストを低く抑えつつ送風性能を向上できる。   According to the present invention, the fluid generated from the leading edge to the trailing edge of the blade when the main plate is rotated in a predetermined direction by curving the blade cross section so as to protrude in the counter-rotating direction of the main plate. Can be directed to the curved portion of the wing. Therefore, by forming the curved portion near the center of the blade in the rotation axis direction, the flow of fluid can be directed to the vicinity of the center of the blade in the rotation axis direction. Therefore, the relative velocity of the fluid with respect to the blade can be made uniform over the direction of the rotation axis of the blade. Further, by directing the fluid flow to the vicinity of the center of the blade in the rotation axis direction, it is possible to suppress the leakage flow to the blade tip on the side opposite to the main plate in the blade, and to suppress the increase of the blade tip vortex. be able to. Therefore, the blade tip vortex of the blade can be reduced without using a shroud, and the blowing performance can be improved while keeping the cost low.

請求項２に係る発明は、請求項１に記載のものであって、前記翼は、前記主板と反対側の翼端部を前記主板の反回転方向に向くように湾曲された湾曲翼端部を形成されてなることを特徴とする。   The invention according to claim 2 is the invention according to claim 1, wherein the blade is a curved blade end portion curved so that the blade end portion on the opposite side of the main plate faces the counter-rotating direction of the main plate. It is characterized by being formed.

この発明によれば、前記湾曲翼端部を前記主板の反回転方向に向くように湾曲させることで、流体の流れを前記主板と反対方向に寄せることができる。これにより、前記湾曲翼端部に沿って前記翼の前縁（主板の内周側）から後縁（主板の外周側）に向かって流れる流体の速度を速くすることができるため、前記翼の後縁から流出する流体の前記翼に対する相対速度を前記翼の回転軸線方向に渡ってさらに均一化することができる。また、前記湾曲翼端部の反回転方向側の翼面近傍に翼端渦を引き寄せて安定させることができる。   According to this invention, the flow of the fluid can be approached in the opposite direction to the main plate by bending the curved blade end so as to face the counter-rotating direction of the main plate. As a result, the velocity of the fluid flowing from the leading edge (inner peripheral side of the main plate) to the rear edge (outer peripheral side of the main plate) along the curved blade end can be increased. The relative velocity of the fluid flowing out from the trailing edge with respect to the blade can be made more uniform across the rotational axis of the blade. Further, the blade tip vortex can be attracted and stabilized in the vicinity of the blade surface on the anti-rotation direction side of the curved blade tip.

請求項３に係る発明は、請求項２に記載のものであって、前記湾曲翼端部の湾曲箇所の前記回転軸線方向の幅を、前記翼の前縁から後縁にかけて次第に大きくなるようにしたことを特徴とする。   The invention according to claim 3 is the invention according to claim 2, wherein the width of the curved portion of the curved blade tip in the direction of the rotational axis is gradually increased from the leading edge to the trailing edge of the blade. It is characterized by that.

この発明によれば、前記湾曲翼端部で翼端渦が発生した場合であっても、この湾曲翼端部に形成した前記湾曲箇所の凹部（負圧側）に翼端渦を引きつけて、翼端渦を保持することができる。すなわち、翼の前縁から後縁に近づくにつれて、翼端渦は成長して大きくなるが、前記湾曲箇所の回転軸線方向の幅も翼の前縁から後縁にかけて次第に大きくなり、成長した翼端渦を引きつける面が前記主板と反対側の翼端部で確保される。これにより、翼端渦を翼の後縁から放出するまで、翼端渦を前記湾曲箇所に保持することができ、ケーシング等の構造部材に翼端渦が干渉して音を生じるのを抑制することができる。   According to this invention, even when a blade tip vortex is generated at the curved blade tip, the blade tip vortex is attracted to the concave portion (negative pressure side) of the curved portion formed at the curved blade tip. End vortices can be retained. That is, as the blade approaches the trailing edge from the leading edge of the blade, the blade tip vortex grows and becomes large, but the width in the rotational axis direction of the curved portion also gradually increases from the leading edge to the trailing edge of the blade, A surface that attracts the vortex is secured at the blade tip opposite to the main plate. Thus, the blade tip vortex can be held at the curved portion until the blade tip vortex is released from the trailing edge of the blade, and the blade tip vortex interferes with a structural member such as a casing to suppress the generation of sound. be able to.

請求項４に係る発明は、請求項２または請求項３に記載のものであって、前記翼の少なくとも前記主板の外周側に位置する後縁を含む前記主板の同一半径位置における翼断面で、前記湾曲翼端部における回転方向に最も突出する点が、前記翼の主板側根元部よりも回転方向に対して後方に位置することを特徴とする。   The invention according to claim 4 is the one according to claim 2 or claim 3, wherein the blade has a blade cross section at the same radial position of the main plate including a trailing edge located on the outer peripheral side of the main plate. The point that protrudes most in the rotation direction at the curved blade end is located rearward with respect to the rotation direction with respect to the main plate side root portion of the blade.

この発明によれば、前記翼断面で、前記翼端部における回転方向に最も突出する点を前記翼の主板側根元部よりも前記回転方向に対して後方に位置させることで、前記主板と反対側の翼端部に沿う流体の流れを増やすことができるため、前記翼に対する流体の相対速度を前記翼の回転軸線方向にさらに均一化することができる。   According to this invention, in the blade cross section, the point that protrudes most in the rotation direction at the blade tip is positioned rearward with respect to the rotation direction with respect to the main plate side root portion of the blade, and thus opposite to the main plate. Since the flow of fluid along the side blade tip can be increased, the relative velocity of the fluid with respect to the blade can be further uniformized in the direction of the rotation axis of the blade.

請求項５に係る発明は、請求項２から請求項４のいずれかに記載のものであって、前記湾曲翼端部を、前記翼のその他の部分よりも柔軟な樹脂材料で形成したことを特徴とする。
この発明によれば、前記翼の旋回時に生じる翼端渦が前記湾曲翼端部に衝突したときに、前記翼端渦のエネルギーを前記湾曲翼端部でダンピングして、渦のエネルギーを吸収して小さくすることができる。従って、前記翼端渦による騒音をより効果的に抑制することができる。さらに、前記翼がアンダーカット形状を有していても、無理抜き成型することが可能となり、効率よく生産することができる。 The invention according to claim 5 is the invention according to any one of claims 2 to 4, wherein the curved blade end portion is formed of a resin material that is more flexible than other portions of the blade. Features.
According to the present invention, when a tip vortex generated when the blade is swung collides with the curved blade tip, the energy of the blade tip vortex is dumped at the curved blade tip to absorb the energy of the vortex. Can be made smaller. Therefore, noise due to the blade tip vortex can be more effectively suppressed. Furthermore, even if the wing has an undercut shape, it can be forcibly punched and can be produced efficiently.

請求項６に係る発明は、請求項５に記載のものであって、前記柔軟な樹脂製材料は、前記翼を使用回転数で回転させたときに、前記翼の周囲に設けられる構造部材との非接触状態を維持し得る硬さを有していることを特徴とする。
この発明によれば、前記主板と反対側の翼端部が回転の遠心力によって前記構造部材に近づくように変位しようとしても、その変形量が前記構造部材に接触しない範囲に限定されるので、前記湾曲翼端部と構造部材との衝突を防止することができる。 The invention according to claim 6 is the invention according to claim 5, wherein the flexible resin material includes a structural member provided around the wing when the wing is rotated at a use rotational speed. It has the hardness which can maintain the non-contact state of.
According to the present invention, even if the blade end opposite to the main plate is about to be displaced so as to approach the structural member by the centrifugal force of rotation, the deformation amount is limited to a range not contacting the structural member. Collision between the curved blade tip and the structural member can be prevented.

請求項７に係る発明は、空気調和機であって、請求項１から請求項６のいずれかに記載の遠心ファンを備えることを特徴とする。
この発明によれば、渦による騒音を抑制して空力損失を抑えることのできる遠心ファンを用いることができるので、快適性や利便性を高めることができる。 The invention according to claim 7 is an air conditioner, comprising the centrifugal fan according to any one of claims 1 to 6.
According to this invention, since the centrifugal fan which can suppress the noise by a vortex and can suppress aerodynamic loss can be used, comfort and convenience can be improved.

請求項１に係る発明によれば、前記翼に対する流体の相対速度を前記翼の回転軸線方向に渡って均一化することができ、翼端渦の増大を抑制することができ、コストを低く抑えつつ送風性能を向上できる。
請求項２に係る発明によれば、前記翼の外周部から流出する流体の前記翼に対する相対速度を前記翼の回転軸線方向に渡ってさらに均一化することができる。また、前記湾曲翼端部の反回転方向側の翼面近傍に翼端渦を引き寄せることができる。 According to the first aspect of the present invention, the relative velocity of the fluid with respect to the blade can be made uniform over the direction of the rotation axis of the blade, the increase of the blade tip vortex can be suppressed, and the cost can be kept low. The air blowing performance can be improved.
According to the invention which concerns on Claim 2, the relative velocity with respect to the said wing | blade of the fluid which flows out from the outer peripheral part of the said wing | blade can be made further uniform over the rotating shaft direction of the said wing | blade. Further, the blade tip vortex can be drawn near the blade surface on the anti-rotation direction side of the curved blade tip.

請求項３に係る発明によれば、翼端渦を翼の後縁から放出するまで、翼端渦を前記湾曲箇所に保持することができ、ケーシング等の構造部材に翼端渦が干渉して音を生じるのを抑制することができる。
請求項４に係る発明によれば、前記翼に対する流体の相対速度を前記翼の回転軸線方向にさらに均一化することができる。 According to the invention of claim 3, the blade tip vortex can be held at the curved portion until the blade tip vortex is released from the trailing edge of the blade, and the blade tip vortex interferes with a structural member such as a casing. Generation of sound can be suppressed.
According to the invention which concerns on Claim 4, the relative velocity of the fluid with respect to the said wing | blade can be made further uniform in the rotating shaft direction of the said wing | blade.

請求項５に係る発明によれば、前記翼端渦による騒音をより効果的に抑制することができる。さらに、前記翼がアンダーカット形状を有していても、無理抜き成型することが可能となり、効率よく生産することができる。   According to the invention which concerns on Claim 5, the noise by the said blade tip vortex can be suppressed more effectively. Furthermore, even if the wing has an undercut shape, it can be forcibly punched and can be produced efficiently.

請求項６に係る発明によれば、前記主板と反対側の翼端部が回転の遠心力によって前記構造部材に近づくように変位しようとしても、前記主板と反対側の翼端部と構造部材との衝突を防止することができる。
請求項７に係る発明によれば、快適性や利便性を高めることができる。 According to the invention which concerns on Claim 6, even if it is going to displace so that the wing end part on the opposite side to the said main plate may approach the said structural member by the centrifugal force of rotation, the wing end part on the opposite side to the said main plate, and a structural member, Can be prevented.
According to the invention concerning Claim 7, comfort and convenience can be improved.

以下、この発明の実施の形態における遠心ファンおよびこれを用いた空気調和機について図面と共に説明する。図１は本発明の第１の実施の形態における遠心ファンの概略斜視図である。同図に示すように、本実施の形態における遠心ファン１は、回転軸線Ｏ周りに所定方向Ｐ（この場合は反時計回り）に回転する略円盤状の主板１１と、該主板１１の中心部に前記回転軸線Ｏを一致させて配設される略円筒状のボス３と、該ボス３の外周側に配設される複数のファンブレード（翼）４とを備えている。   Hereinafter, a centrifugal fan and an air conditioner using the centrifugal fan according to embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a schematic perspective view of a centrifugal fan according to a first embodiment of the present invention. As shown in the figure, the centrifugal fan 1 according to the present embodiment includes a substantially disc-shaped main plate 11 that rotates about a rotation axis O in a predetermined direction P (in this case, counterclockwise), and a central portion of the main plate 11. And a plurality of fan blades (blades) 4 disposed on the outer peripheral side of the boss 3.

前記ファンブレード４について図２を用いて説明する。図２は図１に示す遠心ファンのファンブレード４についての斜視図である。同図に示すように、前記ファンブレード４は、
主板１１から立ち上がり、かつ該主板１１の径方向内方から外方へ延在するように設けられ、該主板１１に前記回転軸線を中心として環状配置されている。そして、前記ファンブレード４には、前記主板１１の外周側に位置する後縁７を含む前記主板１１の同一半径位置における翼断面が前記主板１１の反回転方向（Ｐ方向の反対方向）に突出するように湾曲されてなる（この湾曲された部位を湾曲部１０と称す）。本実施の形態においては、この湾曲部１０をファンブレード４の前縁６側から後縁７に渡り回転軸線方向中央付近に形成している。さらに、このファンブレード４の湾曲部１０の湾曲度合い（曲率）は、その前縁６から後縁７にかけて次第に大きくなっている。 The fan blade 4 will be described with reference to FIG. FIG. 2 is a perspective view of the fan blade 4 of the centrifugal fan shown in FIG. As shown in the figure, the fan blade 4 is
The main plate 11 is provided so as to stand up from the main plate 11 and extend radially inward from the main plate 11. The main plate 11 is annularly arranged around the rotation axis. In the fan blade 4, the blade cross section at the same radial position of the main plate 11 including the rear edge 7 located on the outer peripheral side of the main plate 11 protrudes in the counter-rotating direction of the main plate 11 (opposite direction to the P direction). (This curved portion is referred to as a bending portion 10). In the present embodiment, the curved portion 10 is formed from the front edge 6 side of the fan blade 4 to the rear edge 7 in the vicinity of the center in the rotational axis direction. Further, the degree of curvature (curvature) of the curved portion 10 of the fan blade 4 gradually increases from the front edge 6 to the rear edge 7 thereof.

このように構成された遠心ファン１の作用について説明する。前記遠心ファン１の主板１１を所定方向（この場合はＰ方向、反時計回り）に回転させて、前記ファンブレード４を旋回させることで、前記ファンブレード４の前縁６側に前記主板１１と反対側（上流側）から流体（この場合は空気）を流入させて、ファンブレード４の前縁６側から後縁７側に向けて、ファンブレード４、４…の間から前記流体を送り出すことができる。   The operation of the centrifugal fan 1 configured as described above will be described. The main plate 11 of the centrifugal fan 1 is rotated in a predetermined direction (in this case, P direction, counterclockwise), and the fan blade 4 is swung so that the main plate 11 and the front edge 6 side of the fan blade 4 are rotated. The fluid (in this case, air) flows in from the opposite side (upstream side), and the fluid is sent out from between the fan blades 4, 4... Toward the rear edge 7 side from the front edge 6 side of the fan blade 4. Can do.

そして、前記主板１１を所定方向Ｐに回転させた際に、前記ファンブレード４の前縁６から後縁７にかけて発生する流体の流れを、前記ファンブレード４に形成した湾曲部１０により、ファンブレード４の回転軸線方向中央付近に向けることができる（矢印Ｑ参照）。これにより、前記ファンブレード４からの流体の吹き出し速度を前記ファンブレード４の回転軸線方向中央付近で速めることができる。その結果、前記ファンブレード４に対する流体の相対速度を前記ファンブレード４の回転軸線方向に渡って均一化することができる。すなわち、主板１１と反対側の相対速度ＷＨと主板１１側の相対速度ＷＬとを略同等の大きさにすることができる。   Then, when the main plate 11 is rotated in the predetermined direction P, the flow of the fluid generated from the front edge 6 to the rear edge 7 of the fan blade 4 is caused by the curved portion 10 formed in the fan blade 4 to 4 can be directed to the vicinity of the center of the rotation axis direction of 4 (see arrow Q). Thereby, the blowing speed of the fluid from the fan blade 4 can be increased near the center of the fan blade 4 in the rotation axis direction. As a result, the relative velocity of the fluid with respect to the fan blade 4 can be made uniform over the rotational axis direction of the fan blade 4. That is, the relative speed WH on the side opposite to the main plate 11 and the relative speed WL on the main plate 11 side can be made substantially equal.

また、流体の流れを前記ファンブレード４の回転軸線方向中央付近に向けることで、前記ファンブレード４における前記主板１１と反対側の翼端８への漏れ流れを抑制することができるため、翼端渦Ｓの増大を抑制することができる。従って、シュラウドを用いることなく、前記ファンブレード４の翼端渦Ｓを低減することができ、コストを抑えつつ送風性能を向上できる。
なお、湾曲部１０は、ファンブレード４の少なくとも後縁７を含む部位に形成されている必要があるが、必ずしも前縁６から後縁７に渡って形成されていなくもよい。 Further, since the flow of fluid is directed to the vicinity of the center of the fan blade 4 in the rotation axis direction, the leakage flow to the blade tip 8 on the fan blade 4 opposite to the main plate 11 can be suppressed. An increase in the vortex S can be suppressed. Accordingly, the blade tip vortex S of the fan blade 4 can be reduced without using a shroud, and the blowing performance can be improved while suppressing the cost.
The curved portion 10 needs to be formed in a portion including at least the rear edge 7 of the fan blade 4, but does not necessarily have to be formed from the front edge 6 to the rear edge 7.

以下、本発明の他の実施の形態について説明する。以下の実施の形態において、上述の実施の形態と同様の構成となっている箇所については、同一の符号を付してその説明を適宜省略する。
図３は本発明の第２の実施の形態における遠心ファンの概略斜視図である。図４は図３に示す遠心ファンのファンブレードを示す斜視図である。これらの図に示す遠心ファン２０においては、そのファンブレード２４が、前記主板１１と反対側の翼端２８を前記主板１１の反回転方向（Ｐの逆方向。即ち時計回り方向）に向くように湾曲されてなる湾曲翼端部２９を有している。さらに、この湾曲翼端部２９の軸方向幅を、前記ファンブレード２４の主板１１と反対側の内周端２６から主板１１と反対側の外周端２７にかけて次第に大きくなるように形成している。加えて、ファンブレード２４の少なくとも主板１１の外周側に位置する後縁３７を含む前記主板１１の同一半径位置における翼断面で、前記湾曲翼端部２９における回転方向Ｐに最も突出する湾曲端部突出頂部３３が、前記ファンブレード２４の主板側根元部３９よりも回転方向Ｐに対して後方に位置している。これらの点が第１の実施の形態と異なっている。 Hereinafter, other embodiments of the present invention will be described. In the following embodiments, portions having the same configurations as those of the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted as appropriate.
FIG. 3 is a schematic perspective view of a centrifugal fan according to the second embodiment of the present invention. FIG. 4 is a perspective view showing a fan blade of the centrifugal fan shown in FIG. In the centrifugal fan 20 shown in these drawings, the fan blade 24 faces the blade tip 28 opposite to the main plate 11 in the counter-rotating direction of the main plate 11 (opposite direction of P, ie, clockwise direction). It has a curved blade tip 29 that is curved. Furthermore, the axial width of the curved blade end portion 29 is formed so as to gradually increase from the inner peripheral end 26 opposite to the main plate 11 of the fan blade 24 to the outer peripheral end 27 opposite to the main plate 11. In addition, at the blade cross section at the same radial position of the main plate 11 including the trailing edge 37 positioned at least on the outer peripheral side of the main plate 11 of the fan blade 24, the curved end portion that protrudes most in the rotational direction P at the curved blade end portion 29. The protruding top portion 33 is located rearward with respect to the rotation direction P with respect to the main plate side base portion 39 of the fan blade 24. These points are different from the first embodiment.

本実施の形態における遠心ファン２０の作用について、図５を用いて説明する。この遠心ファン２０にあっては、ファンブレード２４に湾曲翼端部２９を形成したことにより流体の流れを前記主板１１と反対方向に寄せることで、前記主板１１と反対方向の流体の速度を速くすることができる。これにより、前記主板１１と反対側の翼端２８に沿って前記ファンブレード２４の前縁３６（主板１１の内周側）から後縁３７（主板１１の外周側）に向かって流れる流体の速度を速くすることができるため、前記ファンブレード２４の後縁３７から流出する流体の前記ファンブレード２４に対する相対速度を前記ファンブレード２４の回転軸線方向に渡ってさらに均一化することができる。   The operation of the centrifugal fan 20 in the present embodiment will be described with reference to FIG. In the centrifugal fan 20, the curved blade tip 29 is formed on the fan blade 24, so that the fluid flow is moved in the direction opposite to the main plate 11, thereby increasing the speed of the fluid in the direction opposite to the main plate 11. can do. Thereby, the velocity of the fluid flowing along the blade tip 28 on the side opposite to the main plate 11 from the front edge 36 (inner peripheral side of the main plate 11) of the fan blade 24 toward the rear edge 37 (outer peripheral side of the main plate 11). Therefore, the relative velocity of the fluid flowing out from the trailing edge 37 of the fan blade 24 with respect to the fan blade 24 can be made more uniform over the rotational axis direction of the fan blade 24.

さらに、前記湾曲翼端部２９の翼端２８で翼端渦Ｓが発生した場合であっても、前記湾曲翼端部２９の凹部（負圧側、図５の裏面側）に翼端渦Ｓを引きつけて、翼端渦Ｓを保持することができる。すなわち、ファンブレード２４の前縁３６側から後縁３７側に近づくにつれて、翼端渦Ｓは成長して大きくなる。しかしながら、前記湾曲翼端部２９の軸方向幅も前縁３６側から後縁３７側にかけて次第に大きくなるため、成長した翼端渦Ｓを湾曲翼端部２９により前縁３６側から後縁３７側にかけて引きつけておくことができる。これにより、翼端渦Ｓをファンブレード２４の後縁３７から放出するまで、翼端渦Ｓを前記湾曲翼端部２９に保持することができ、ケーシング等の構造部材に翼端渦Ｓが干渉して音を生じるのを抑制することができる。   Further, even when a blade tip vortex S is generated at the blade tip 28 of the curved blade tip portion 29, the blade tip vortex S is applied to the concave portion (negative pressure side, back side of FIG. 5) of the curved blade tip portion 29. The blade tip vortex S can be held by attracting. That is, the blade tip vortex S grows and becomes larger as it approaches the rear edge 37 side from the front edge 36 side of the fan blade 24. However, since the axial width of the curved blade tip 29 gradually increases from the leading edge 36 side to the trailing edge 37 side, the grown blade tip vortex S is caused by the curved blade tip portion 29 to move from the leading edge 36 side to the trailing edge 37 side. It can be attracted through. Thus, the blade tip vortex S can be held on the curved blade tip 29 until the blade tip vortex S is released from the trailing edge 37 of the fan blade 24, and the blade tip vortex S interferes with a structural member such as a casing. Thus, the generation of sound can be suppressed.

加えて、前記主板１１の同一半径位置における翼断面で、前記湾曲翼端部２９における回転方向Ｐに最も突出する湾曲端部突出頂部３３が、前記ファンブレード２４の主板側根元部３９よりも回転方向Ｐに対して後方に位置させることで、前記主板１１と反対側の翼端２８に沿う流体の流れを増やすことができる。このため、前記ファンブレード２４に対する流体の相対速度を前記ファンブレード２４の回転軸線方向にさらに均一化することができる。   In addition, in the blade cross section at the same radial position of the main plate 11, the curved end protruding top 33 that protrudes most in the rotation direction P of the curved blade end 29 rotates more than the main plate side root portion 39 of the fan blade 24. By being positioned rearward with respect to the direction P, the flow of fluid along the blade tip 28 on the side opposite to the main plate 11 can be increased. For this reason, the relative velocity of the fluid with respect to the fan blade 24 can be made more uniform in the direction of the rotation axis of the fan blade 24.

ここで、前記湾曲翼端部２９を、前記ファンブレード２４のその他の部分よりも柔軟な樹脂材料で形成することが好ましい。このようにすると、前記ファンブレード２４の旋回時に生じる翼端渦Ｓが前記湾曲翼端部２９に衝突したときに、前記翼端渦Ｓのエネルギーを前記湾曲翼端部２９でダンピングして、渦Ｓのエネルギーを吸収して小さくすることができる。従って、前記翼端渦Ｓによる騒音をより効果的に抑制することができる。さらに、前記ファンブレード２４がアンダーカット形状を有していても、無理抜き成型することが可能となり、効率よく生産することができる。   Here, it is preferable that the curved blade end portion 29 is formed of a resin material that is more flexible than other portions of the fan blade 24. In this way, when the blade tip vortex S generated when the fan blade 24 swivels collides with the curved blade tip 29, the energy of the blade tip vortex S is damped by the curved blade tip 29, and the vortex The energy of S can be absorbed and reduced. Therefore, noise due to the blade tip vortex S can be more effectively suppressed. Furthermore, even if the fan blade 24 has an undercut shape, it can be forcibly punched and can be produced efficiently.

また、前記柔軟な樹脂製材料は、前記ファンブレード２４を使用回転数で回転させたときに、前記ファンブレード２４の周囲に設けられる構造部材（ケーシング、ベルマウス等）との非接触状態を維持し得る硬さを有していることが好ましい。このようにすると、前記翼端２８が回転の遠心力によって前記構造部材に近づくように変位しようとしても、その変形量が前記構造部材に接触しない範囲に限定されるので、前記翼端２８と構造部材との衝突を防止することができる。   Further, the flexible resin material maintains a non-contact state with structural members (a casing, a bell mouth, etc.) provided around the fan blade 24 when the fan blade 24 is rotated at a used rotational speed. It is preferable to have such a hardness. In this case, even if the blade tip 28 is displaced so as to approach the structural member due to the centrifugal force of rotation, the deformation amount is limited to a range that does not contact the structural member. Collision with the member can be prevented.

このような性質を有する樹脂製材料として、スチレン系熱可塑性エラストマー、塩化ビニル系熱可塑性エラストマー、オレフィン系熱可塑性エラストマー等、耐候性に優れたものを好適に用いることができる。また、物性として、材料の伸び率を５００〜１５００％（３号ダンベル、５００ｍｍ／ｍｉｎ：ＪＩＳ Ｋ ６２５１の場合）とすることが好ましい。   As the resinous material having such properties, a material having excellent weather resistance such as a styrene-based thermoplastic elastomer, a vinyl chloride-based thermoplastic elastomer, and an olefin-based thermoplastic elastomer can be suitably used. Further, as physical properties, it is preferable that the elongation of the material is 500 to 1500% (No. 3 dumbbell, 500 mm / min: in the case of JIS K 6251).

なお、本発明の内容は上述の実施の形態のみに限られるものでないことはもちろんである。例えば、空気調和機としては、換気扇やエアコンといった家電用品に限らず、上述の遠心ファンを備えた空気調和機であればよい。   Of course, the contents of the present invention are not limited to the above-described embodiments. For example, the air conditioner is not limited to home appliances such as a ventilation fan and an air conditioner, and may be an air conditioner including the above centrifugal fan.

本発明の第１の実施の形態における遠心ファンの概略斜視図である。It is a schematic perspective view of the centrifugal fan in the 1st Embodiment of this invention. 図１に示す遠心ファンのファンブレードと、その旋回時に発生する翼端渦や空気の相対速度を示す斜視説明図である。FIG. 2 is a perspective explanatory view showing the fan blades of the centrifugal fan shown in FIG. 1 and the relative velocities of blade tip vortices and air generated when the fan blades turn. 本発明の第２の実施の形態における遠心ファンの概略斜視図である。It is a schematic perspective view of the centrifugal fan in the 2nd Embodiment of this invention. 図３に示す遠心ファンのファンブレードを示す斜視図である。It is a perspective view which shows the fan blade of the centrifugal fan shown in FIG. 図４に示す遠心ファンのファンブレードと、その旋回時に発生する翼端渦や空気の相対速度を示す説明図である。It is explanatory drawing which shows the relative speed of the fan blade of the centrifugal fan shown in FIG. 4, and the tip vortex and air which generate | occur | produce at the time of the rotation. 従来における基本的な遠心ファンについての斜視図である。It is a perspective view about the conventional basic centrifugal fan. 図６に示す遠心ファンのファンブレードと、その旋回時に発生する翼端渦を示す斜視図である。It is a perspective view which shows the fan blade of the centrifugal fan shown in FIG. 図６に示す遠心ファンのファンブレードと、その旋回時における空気の相対速度を示す斜視図である。It is a perspective view which shows the relative speed of the air at the time of the fan blade of the centrifugal fan shown in FIG. 6, and the turning. 従来における改良型の遠心ファン（シュラウドあり）の概略説明図である。It is a schematic explanatory drawing of the conventional improved centrifugal fan (with shroud). 従来における改良型の遠心ファン（シュラウドなし）の概略説明図である。It is a schematic explanatory drawing of the conventional improved centrifugal fan (without shroud). 図１０に示す遠心ファンの断面図である。It is sectional drawing of the centrifugal fan shown in FIG. 図１１に示す遠心ファンの問題点を示す説明図である。It is explanatory drawing which shows the problem of the centrifugal fan shown in FIG.

符号の説明Explanation of symbols

１、２０…遠心ファン
３…ボス
４、２４…ファンブレード
１０…湾曲部
１１…主板
２８…翼端
２９…湾曲翼端部
３３…湾曲翼端部突出頂部
３９…根元部
DESCRIPTION OF SYMBOLS 1, 20 ... Centrifugal fan 3 ... Boss 4, 24 ... Fan blade 10 ... Curved part 11 ... Main plate 28 ... Blade tip 29 ... Curved blade tip 33 ... Curved blade tip protruding top 39 ... Root part

Claims (7)

回転軸線周りに所定方向に回転可能な主板と、該主板から立ち上がり、かつ該主板の径方向内方から外方へ延在するように設けられ、該主板に前記回転軸線周りに配置された複数の翼とを備え、
前記翼の少なくとも前記主板の外周側に位置する後縁を含む前記主板の同一半径位置における翼断面が前記主板の反回転方向に突出するように湾曲されてなり、かつ、その湾曲は前記翼の前縁側から後縁にかけて次第に大きくなっていることを特徴とする遠心ファン。 A main plate rotatable around a rotation axis in a predetermined direction, and a plurality of plates arranged so as to rise from the main plate and extend from the inside in the radial direction of the main plate to the outside, and arranged on the main plate around the rotation axis With wings of
A blade section at the same radial position of the main plate including a trailing edge located at least on the outer peripheral side of the main plate of the wing is curved so as to protrude in the counter-rotating direction of the main plate, and the curvature of the wing is A centrifugal fan characterized by gradually increasing from a front edge side to a rear edge. 前記翼は、前記主板と反対側の翼端部を前記主板の反回転方向に向くように湾曲された湾曲翼端部を形成されてなることを特徴とする請求項１に記載の遠心ファン。   2. The centrifugal fan according to claim 1, wherein the blade is formed with a curved blade end portion which is curved so that a blade end portion on the side opposite to the main plate faces in a counter-rotating direction of the main plate. 前記湾曲翼端部の湾曲箇所の前記回転軸線方向の幅を、前記翼の前縁から後縁にかけて次第に大きくなるようにしたことを特徴とする請求項２に記載の遠心ファン。   The centrifugal fan according to claim 2, wherein a width of the curved portion of the curved blade end portion in the direction of the rotation axis is gradually increased from a front edge to a rear edge of the blade. 前記翼の少なくとも前記主板の外周側に位置する後縁を含む前記主板の同一半径位置における翼断面で、前記湾曲翼端部における回転方向に最も突出する点が、前記翼の主板側根元部よりも回転方向に対して後方に位置することを特徴とする請求項２または請求項３に記載の遠心ファン。   In the blade cross section at the same radial position of the main plate including the trailing edge located at least on the outer peripheral side of the main plate of the blade, the point that protrudes most in the rotational direction at the curved blade end is from the base portion on the main plate side of the blade. 4. The centrifugal fan according to claim 2, wherein the centrifugal fan is located rearward with respect to the rotation direction. 前記湾曲翼端部を、前記翼のその他の部分よりも柔軟な樹脂材料で形成したことを特徴とする請求項２から請求項４のいずれかに記載の遠心ファン。   The centrifugal fan according to any one of claims 2 to 4, wherein the curved blade end portion is formed of a resin material that is softer than other portions of the blade. 前記柔軟な樹脂製材料は、前記翼を使用回転数で回転させたときに、前記翼の周囲に設けられる構造部材との非接触状態を維持し得る硬さを有していることを特徴とする請求項５に記載の遠心ファン。   The flexible resin material has a hardness capable of maintaining a non-contact state with a structural member provided around the wing when the wing is rotated at a rotational speed of use. The centrifugal fan according to claim 5. 請求項１から請求項６のいずれかに記載の遠心ファンを備えることを特徴とする空気調和機。
An air conditioner comprising the centrifugal fan according to any one of claims 1 to 6.
JP2004176867A 2004-06-15 2004-06-15 Centrifugal fan and air conditioner using the same Expired - Fee Related JP4308718B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2004176867A JP4308718B2 (en) 2004-06-15 2004-06-15 Centrifugal fan and air conditioner using the same
KR1020040085044A KR100635851B1 (en) 2004-06-15 2004-10-22 A centrifugal fan and a air conditioner utilizing it
CNB2005100052543A CN100504073C (en) 2004-06-15 2005-02-03 Eccentric fan and air conditioner therewith

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004176867A JP4308718B2 (en) 2004-06-15 2004-06-15 Centrifugal fan and air conditioner using the same

Publications (2)

Publication Number Publication Date
JP2006002585A true JP2006002585A (en) 2006-01-05
JP4308718B2 JP4308718B2 (en) 2009-08-05

Family

ID=35718485

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004176867A Expired - Fee Related JP4308718B2 (en) 2004-06-15 2004-06-15 Centrifugal fan and air conditioner using the same

Country Status (3)

Country Link
JP (1) JP4308718B2 (en)
KR (1) KR100635851B1 (en)
CN (1) CN100504073C (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100158677A1 (en) * 2008-12-22 2010-06-24 Sanyo Denki Co., Ltd. Axial flow fan
WO2014199498A1 (en) * 2013-06-13 2014-12-18 三菱重工業株式会社 Impeller and fluid machine
KR20150136935A (en) * 2014-05-28 2015-12-08 엘지전자 주식회사 Centrifugal fan
WO2016042818A1 (en) * 2014-09-18 2016-03-24 三菱重工業株式会社 Centrifugal impeller and centrifugal compressor
KR20160085185A (en) * 2015-01-07 2016-07-15 한온시스템 주식회사 Impeller of a blower arrangement for an air-conditioning system of a motor vehicle
JP2016223403A (en) * 2015-06-03 2016-12-28 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Turbo fan and air blower using the same
JP2021005965A (en) * 2019-06-27 2021-01-14 三菱電機株式会社 Rotary electric machine
CN116007074A (en) * 2022-12-10 2023-04-25 丽水学院 Automatic air treatment device of dehumidification

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100765199B1 (en) * 2006-10-09 2007-10-09 삼성전자주식회사 Centrifugal fan and air conditioner having the same
JP4994421B2 (en) * 2009-05-08 2012-08-08 三菱電機株式会社 Centrifugal fan and air conditioner
KR101977939B1 (en) 2012-11-13 2019-05-14 엘지전자 주식회사 A centrifugal fan and an air conditioner utilizing it
EP2829733B1 (en) 2013-05-10 2021-01-27 Lg Electronics Inc. Centrifugal fan
KR101645178B1 (en) 2013-05-10 2016-08-03 엘지전자 주식회사 Centrifugal fan and manufacturing method thereof
KR102108442B1 (en) * 2018-03-20 2020-05-12 주식회사 씨아이에코텍 An apparatus for collecting film
WO2019244344A1 (en) * 2018-06-22 2019-12-26 三菱重工エンジン＆ターボチャージャ株式会社 Rotor and centrifugal compression machine provided with said rotor
CN109322850A (en) * 2018-11-02 2019-02-12 浙江工业大学 A kind of vortex pump impeller
JP7217176B2 (en) * 2019-03-04 2023-02-02 新晃工業株式会社 Blade structure of centrifugal blower
EP3738634A1 (en) * 2019-05-16 2020-11-18 Löwenstein Medical Technology S.A. Breathing therapy device and fan for breathing therapy device
CN110725808B (en) * 2019-10-31 2021-03-02 中国科学院工程热物理研究所 Centrifugal impeller blade, configuration method and centrifugal compressor
KR102467279B1 (en) * 2020-12-02 2022-11-16 엘지전자 주식회사 Centrifugal fan
CN113217458B (en) * 2021-05-28 2022-09-02 宁波方太厨具有限公司 Impeller, fan system applying impeller and range hood

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3391319B2 (en) 1999-12-01 2003-03-31 ダイキン工業株式会社 Centrifugal fan and air conditioner equipped with the centrifugal fan
JP2001159396A (en) 1999-12-03 2001-06-12 Daikin Ind Ltd Centrifugal fan and air conditioner equipped with the same

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8770943B2 (en) * 2008-12-22 2014-07-08 Sanyo Denki Co., Ltd. Axial flow fan
US20100158677A1 (en) * 2008-12-22 2010-06-24 Sanyo Denki Co., Ltd. Axial flow fan
US9874219B2 (en) 2013-06-13 2018-01-23 Mitsubishi Heavy Industries, Ltd. Impeller and fluid machine
WO2014199498A1 (en) * 2013-06-13 2014-12-18 三菱重工業株式会社 Impeller and fluid machine
KR20150136935A (en) * 2014-05-28 2015-12-08 엘지전자 주식회사 Centrifugal fan
KR102227374B1 (en) * 2014-05-28 2021-03-11 엘지전자 주식회사 Centrifugal fan
WO2016042818A1 (en) * 2014-09-18 2016-03-24 三菱重工業株式会社 Centrifugal impeller and centrifugal compressor
KR101667478B1 (en) * 2015-01-07 2016-10-28 한온시스템 주식회사 Impeller of a blower arrangement for an air-conditioning system of a motor vehicle
KR20160085185A (en) * 2015-01-07 2016-07-15 한온시스템 주식회사 Impeller of a blower arrangement for an air-conditioning system of a motor vehicle
JP2016223403A (en) * 2015-06-03 2016-12-28 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Turbo fan and air blower using the same
JP2021005965A (en) * 2019-06-27 2021-01-14 三菱電機株式会社 Rotary electric machine
JP7002499B2 (en) 2019-06-27 2022-01-20 三菱電機株式会社 Rotating machine
CN116007074A (en) * 2022-12-10 2023-04-25 丽水学院 Automatic air treatment device of dehumidification
CN116007074B (en) * 2022-12-10 2024-06-04 丽水学院 Automatic air treatment device of dehumidification

Also Published As

Publication number Publication date
KR100635851B1 (en) 2006-10-19
KR20050119071A (en) 2005-12-20
CN100504073C (en) 2009-06-24
JP4308718B2 (en) 2009-08-05
CN1712733A (en) 2005-12-28

Similar Documents

Publication Publication Date Title
JP4308718B2 (en) Centrifugal fan and air conditioner using the same
JP6428833B2 (en) Propeller fan
JP5059071B2 (en) Blower
JP4501575B2 (en) Axial blower
EP2570677B1 (en) Axial flow blower
JP6914371B2 (en) Axial blower
JP5562566B2 (en) Wing body for fluid machinery
JPWO2017216937A1 (en) Impeller and axial blower
WO2018020708A1 (en) Propeller fan and fluid feeding device
CN107882772B (en) Reversible blowing fan
JP6066691B2 (en) Propeller fan and air conditioner using the propeller fan
JP2009068361A (en) Blower
JP5418538B2 (en) Blower
KR20080019521A (en) Propeller fan
JP2006090178A (en) Blower impeller
JP2006322378A (en) Blower impeller
JP2007247494A (en) Diagonal flow blower impeller
JP2010236372A (en) Axial blower, air conditioner, and ventilation fan
JPH08240197A (en) Axial-flow fan
JP2004011423A (en) Air flow control structure of air blowing section
JP2006002584A (en) Propeller fan and air conditioner using the same
JP6414268B2 (en) Propeller fan
JP5114845B2 (en) Blower impeller
JP4492060B2 (en) Blower impeller
KR100484824B1 (en) An axial flow fan

Legal Events

Date Code Title Description
A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20071011

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20071016

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080116

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20080401

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080701

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20090407

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20090501

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120515

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130515

Year of fee payment: 4

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees